Automatic turret lathe



AUTOMAT I C TURR ET LATHE Filed May 29, 1936 2 Sheets-Sheet l Oct. 5, 1937., F. POPPENSIEKER AUTOMATIC TURRET LATHE FiledMay 29, 1956 2 Sheets-Sheet 2 Patented Oct. 5, 1937 v UNITED STATES AUTOMATIC TURRET LATHE Fritz Poppensieker, Cologne, Germany Application May 29, 1936, Serial No. 82,566 In Germany April 18, 1936 7 Claims (01. 29-42) My invention relates to'turret lathes and more especially to the means for driving the longitudinal slide in such lathes. turret lathes the longitudinal slide which carries the tools is generally driven by means of a cam .drum. As a rule such cam drums have a relatively large circumference as apart from the working c? the quick return and the quick advance cams have to be accommodated. This question of size becomes particularly vital when a longitudinal slide is provided with a turret head and has to execute a series of forward and rearward motions during one rotation of the cam drum.

In this case a corresponding number of workingcams and idling cams have to be provided so that the cam drum becomes correspondingly large and heavy. I

The present invention relates to a drive for the longitudinal slide in which the said disadvantage is avoided. The .invention resides in that the drive of the longitudinal slide for the working motion is derived from the customary cam drum but the idling movements are effected at an appreciably higher speed by means of a hydraulic gear. This has the advantage that only one feed cam or only a few feed cams have to be provided so that the diameter of the cam drum can be correspondingly small. Moreover, the machine is simplified. Due to the smallness of the drum, it is also more readily possible to keep available for any frequently occurring series of operations a cam drum equipped with a corresponding set of cams and to mount'the appropriate cam drum on the lathe as required. It should also be mentioned that the working cams which are retained are comparatively simple in form, whereas the quick return and quick advance cams which are dispensed with are costly, due to the curved portions which have to be provided'in order to obtain a smooth motion of the cam roller. In order to save time before the hydraulic rapid return and after the hydraulic rapid forward motion, in both cases an abrupt or short high speed movement can be provided for the cam drum which on the one hand releases the cam roller from the cam for the high speed return immediately after the working operation is completed, and on the other hand allows the cam roller to come into position as quickly as possible for the commencement of the new working operation after the termination of the idle movement. If both fi'fqvements were effected at the slow working speed, then a very considerable loss of time would be incurred in the case of a slide with a-turret head.

One embodiment of the invention is shown by Hitherto in automatic way of example in the accompanying drawings, in which:

Fig. 1 shows a front elevation of a single spindle automatic lathe,

Fig. 2 is a side view from the right, Fig. 3 shows the cam drum in side elevation, Fig. 4 shows an end view of the drum and Fig. 5 shows' diagrammatically the combined mechanical and hydraulic gearing.

As seen from Figs. 1 and 2 the machine is constructed as follows:

Erected at the right and left hand ends of the box base I are the standards 2 and 3 which are connected by an intermediate member 4. At the top the two standards are connected by a beam 5 which is disposed towards the rear. The machine is provided with two longitudinal slides 6 and I, the former being carried on the intermediate member 4 while the slide 1 which is disposed above the slide 6 and carries the turret 8 is suspended from the connecting beam 5. The working spindle 9 is mounted in the left hand standard 2 in which are accommodated the mechanisms for driving the spindle 9 and the lower slide 6. Accommodated in the right hand Standard'3 is the cam drum Ill which drives the upper longitudirliial slide 1 byway of the, intermediate member The cam drum Ill (Figs. 3 and 4) carries a series of working cams l2 to I! which serve for advancing the longitudinal slide 1 in the consecutive working operations by means of the cam roller 18 and the intermediate member II, in accordance with the tool on the turret head 8 which is in working position. In Figs. 3 and 4 the cam roller iii in the full line position is located between two consecutive cam sections [3 and M. The cam drum is thus in the interval between two working periods, 1. e., the high speed position.

In order to explain the manner in which the longitudinal slide is driven, the position of the cam roller on passing through the cam l2 to the cam I3 (Fig. 3) will be described.

At the end of one working stroke corresponding to the cam H, the cam roller is in the position l9. At this moment one of the adjustable lugs 20 on the disc 2| connected with the cam is attached, together with the longitudinal slide 1. A stop device which will be described subsequently then switches oil. the hydraulic gearing at the desired moment. In this way the cam roller l8 takes up the position 24. By means of a control shaft 25 and lug 26 (Figs. 1 and 2) the control valve 21 is then actuated, whereby the slide I is again advanced hydraulically. A stop device described below then switches ofl' the hydraulicgearing so as to cause the cam roller l8 to assume the position 28 (Fig. 3). Simultaneously with this switching off of the hydraulic gearing. a mechanical high speed movement of the drum is initiated. Consequently the drum is brought into a position corresponding to the position 29 of the cam roller I8 so that the roller is brought just into engagement with the cam l3. On the further high speed rotation of the drum one of the adjustable lugs 38 on the disc 2| cuts out the high speed movement, whereupon the drum continues to rotate from the position 3| of the cam roller at the working speed.

The manner in which the mechanical and hydraulic gears co-operate is indicated in Fig. 5. The common drive of the mechanical gearing and hydraulic gearing is derived from the motor 32. The mechanical drive is divided into a slow working movement and a high speed movement. The slow working movement is produced by the following elements:--

From the motor 32, the drive is transmitted by way of the gear wheels 33, shaft 34 and bevel gear wheels 35 to the change wheels 36 by means of which the working speed is adjusted. From the change wheels 36, the drive is transmitted by way of shaft 31 over a free wheel or unidirectional coupling 38, releasable coupling 50, worm shaft 39 and worm wheel 48 to the cam drum l and disc 2|. Also the control shaft 25 is driven from the change wheels 36 by way 'of shaft 31, free wheel or uni-directional coupling 4|, worm shaft 42 and worm gear 43.

The mechanical high speed motion is obtained in the following way. From the motor 32, the drive is transmitted to the coupling wheels 46 and 4! by way of gear wheels 33, shaft 34 and bevel gears 45. When the couplings 48 and 49 are engaged, the high speed drive is imparted on the one hand to the cam drum I 8 and on the other hand to the control shaft 25. This high speed motion is possible by over-running the free wheel couplings 38 and 4|. It should be mentioned that during the high speed drive of the cam drum I0 the coupling 50 is also engaged. The hydraulic drive is derived from the pump which is driven by the shaft 34.

At the end of the working movement of the drum Hi there is, as. previously mentioned, an abrupt advance of the drum corresponding to a.

relative change in position of the cam roller I8 from l9 to (Fig. 3). This movement is obtained as follows: As soon as the drum III has assumed the position l9 with respect to the cam roller l8, then the lug 26 on the disc 2| actuates a linkage 52 (FIG. 5).

In this way the detent lever 531s moved downwardly against the action of a spring. The member 54 which was supported by a shoulder on the detent lever 531s thus released and by means of the spring 55 is urged downwardly into the position shown in Fig.

5. At the same time the member 56 disposed beneath it is also moved downwardly. The lower member 56 is retained in this position by means of a catch 51. The member 56 engages the double sided coupling sleeve 58 whereby owing to the downward movement of the coupling the drive of the cam drum I8 is broken at the cou- -.cam 69.

pling 56 and the rapid advance is occasioned by way of coupling wheel 59 under the control'of the roller 6| in the following way:

A driving connection is provided between the coupling wheel 59 and the wheel 68 which is rigidly connected with -the'control roller 6| which is driven from the shaft 34 by way of the bevel gears 62 and the clutch 63. For each abrupt movement of the cam drum Hi there is one rotation of the control roller 6|, whereupon the roller automatically comes to rest. The rotation of the control roller 6| is initiated by the downward movement ofthe member 54, whereby the clutch 63 is engaged by means of a rod 64 and arm 65. By the rotation of the'control roller 6| the cam drum I0 is rotated at high speed by way of gear wheels 60 and 59, shaft 39 and worm gearing 49 until the roller l8 moves from position |9 to position 22. Towards the end of this movement of the control roller 6|, the member 54 is lifted again against the action of the spring 55 and spring 68 by means of the cam 66. Before the completion of one rotation of the control roller 6| the member 54 engages the collar 6'| on the shaft 64 and releases the clutch 63 by way of arm 65, so. that the control roller 6| comes to rest.

The hydraulic high speed return movement corresponding to displacement of the cam roller from 22 to 24 (Fig. 3) is initiated during the operation of the control roller 6| by means of the (Fig. 5.) age II this cam actuates the rotary valve 21.

' Oil under pressure from the pump 5| then takes the following path. It first flows through the conduit "I2, through the valve 21 and through the conduit 13 to in front ,of the piston 23. The oil behind the piston flows through the conduit 8| and valve 2! into the conduit 88. The slide 1- is thus withdrawn to the right. By means of the lug 15 the lever 14 mounted on the intermediate member II is rocked to the left. When the lever 14 is rocked, the control shaft TI is rotated by way of a pair of bevel gears 16. The control shaft I1 then performs two functions. On the one hand, it actuates the rotary valve 21 by way of lever 18 and linkage 19. The oil under pressure then flows from conduit 12 through valve 21 into the conduit 80 and the high speed retraction of the slide 1 is terminated. On the other hand, the control shaft 11 throws in a clutch 84 by way of lever 82 and linkage 83. This clutch 84 is driven by the bevel gears I93 and shaft I04. The clutch '84 is a. single rotation clutch which automatically disengages after one rotation. During this rotation of the clutch 84, the turret head 8 is indexed one step by way of gear wheels 85 and 86, the long indexing drum 8! and the transmission gears 88 by way of a Geneva cross mechanism not shown. At the same time the roller 92 carrying the lugs is also rotated a corresponding amount by means of wheels 81, shaft 89, transmission gearing 96 and shaft 9|. Due to this rotation of the roller 92, two new lugs are brought into the path of the lever 14. The various pairs of lugs on the roller 92 are adjusted to limit the hydraulic forward and'return motions in accordance with the operations to be performed by the turret head 8.

A lug 26 disposed on the disc 93 (Fig. 5) on the control shaft 25 serves for initiating the hydraulic advance corresponding to the cam roller |8.moving from position 24 to position 28 (Fig. 3). This ing 26 controls the valve 21 sothat the oil under pressure passes from the conduit 12 through the valve 21 into the conduit 8| and to the right hand By way of lever 18 and linkv regarded only as examples.

side of the piston 23. Consequently the piston 23 moves to the left and displaces the longitudinal slide 1 into the working position.

The oil in front of the piston escapes through conduit "and valve 21 into the conduit 80. To-

wards the end of the advance of the longitudinal slide, the stop 95 rocks the lever I4 to the right into the position shown in Fig. 5. Thereupon by way of the bevel gear 16, control shaft 11, lever 10 and linkage I9, the rotary valve 21 is so positioned that the pressure liquid operates on an auxiliary piston 01 by way of conduit 12, valve 21 and conduit 96. Consequently the auxiliary piston 91 is urged downwardly against the action of a spring until the oil under pressure passes through conduit 98 into the conduit 80. On depressing the auxiliary piston 91, the catch 51 which is connected thereto releases the member 56. Due to the action of the spring 68, the member 56 is moved upwardly and thus brings the double coupling sleeve 58 into engagement with the coupling 50. In this way the cam drum is then driven in the manner previously described and the control roller 6| is released.

In order to obtain the high speed motion of the cam drum from the cam roller position 20 to the cam roller position 3|, during the abovementioned single rotation of the control roller BI the cam 90 rocks the lever I00 about the pin IM to such an extent as to engage the coupling 48. Thus, as both couplings 48 and 50 are in engagement, the cam drum I0 is rotated at high speed for a period corresponding to the movement of the cam roller from position 28 to position 3|. To terminate this brief high speed motion of the cam drum I0 when the cam roller assumes the position 3|, the coupling 48 is disengaged again by means.

of the adjustable lugs 30 on, the disc 2I by way of linkage I02. Then the high speed motion of short duration is replaced by the slow working operation. During the working and high speed motions of the cam drum I0 as portrayed above, the control shai t 25 has rotated only at the working speed.

Consequently after a complete rotation of the cam drum the control shaft has still not made a complete rotation. In order to save time the control shaft 25 must complete the rotation at high speed. This is effected by actuating the coupling 49 by means of lugs I05 and I06 on the disc I01 on the control shaft 25 by way of a linkage I08.

All the gear mechanisms described are to be The necessary high speed and rapid movements of the tool slide on the one hand and the cam drum on the other hand, as well as the other control movements, could be effected by other means in order to obtain after the working movements of the longitudinal slide as determined by the working cams on the cam drum, the appreciable quicker hydraulic idle movements of the hydraulic as well as the rapid and high speed movements of the cam drum.

Having now particularly described and ascertained the nature of my said invention and in what manner the same is to be performed, I declare that what I claim is:-

1. In an automatic turret lathe means for imparting the working and idling motions to the longitudinal tool slide comprising a roller associated with said slide, a drum carrying cams adapted to engage-said roller only for the work ing motion and to advance the slide slowly during the working motion and liquid-actuated means adapted to operate on said slide when said roller is not operatively engaged by the cam drum working motion and a hydraulic gearing adapted to operate on said slide when said roller is not operatively engaged by the cam drum and to impart to the slide the high speed retraction and advance of the idling motion.

3. In an automatic turret lathe means for imparting the working and idling motions to the longitudinal tool slide comprising a roller associated with said slide, a drum carrying cams adapted to engage said roller only for the working motion and to advance the slide slowly during the working motion and a hydraulic gearing adapted to operate on said slide when said roller is not operatively engaged by the cam drum and to impart to the slide the high speed retraction and advance of the idling motion, and means for imparting an abrupt movement to the drum at the end of the high speed advance to bring the cam roller into engagement with a cam for the next working operation.

4. In an automatic turret lathe means for imparting the working and idling motions to the longitudinal tool slide comprising a roller associated with said slide, a drum carrying cams adapted to engage said roller only forthe working motion and to advance the slide slowly during the working motion, means for imparting an abrupt movement to the drum at the end of the working motion and a hydraulic gearing adapted to operate on said slide when said roller is not operatively engaged by the cam drum and to impart to the slide the high speed retraction and advance of the idling motion, and means for imparting an abrupt movement to the drum at the end of the high speed advance to bring the cam roller into engagement with a cam for the next working operation.

5. In an automatic turret lathe means for imparting the working and idling motions to the longitudinal tool slide comprising a roller associated with said slide, a drum carrying cams adapted to engage said roller only for the working motion and to advance the slide slowly during the working motion, means for imparting an abrupt rotary movement to the drum at the end of the working motion and a hydraulic gearing adapted to operate on said slide when said roller is not operatively engaged by the cam drum and to impart to the slide the high speed retraction and advance of the idling motion.

6. In an automatic turret lathe means for imparting the working and idling motions to the drum at the end of the high speed advance to bring the cam roller into. engagement with a cam for the next working operation.

1 7. In an automatic turret lathe means for imparting the working and idling motions to the longitudinal tool slide comprising a roller associated with said slide, a drum carrying cams adapted to engage said roller only for the working motion and to advance the slide slowly during the working motion, means for imparting an abrupt rotary movement to the drum at the end oi the working motion and a hydraulic gearing 

